JP4249380B2

JP4249380B2 - Air conditioner

Info

Publication number: JP4249380B2
Application number: JP2000247383A
Authority: JP
Inventors: 慎一若本; 広有柴; 守也宮本; 康文畑村
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2000-08-17
Filing date: 2000-08-17
Publication date: 2009-04-02
Anticipated expiration: 2020-08-17
Also published as: JP2002061966A

Description

【０００１】
【発明の属する技術分野】
この発明は、空気調和装置に関するものである。
【０００２】
【従来の技術】
従来の空気調和装置として、減圧器と室内側熱交換器との間に気液分離器を設け、減圧器により減圧した低圧冷媒を気液分離し（約２０％がガス冷媒で残り約８０％が液冷媒となる）、この分離したガス冷媒（このガス冷媒は潜熱を持たないため冷凍能力にはあまり寄与しない）を直接圧縮機の吸入側に流通させ、室内側熱交換器へはガス冷媒を流通させずに液冷媒のみを流通させ、このようにすることにより室内側熱交換器および接続配管などの低圧側配管での圧力損失を低減して、冷凍能力の向上を図ったものがある。このような従来の空気調和装置としては、例えば、特開平９−３１０９２５号公報に記載されたものが知られている。
この空気調和装置では、同公報に記載されているように気液分離器から圧縮機吸入側の低圧ガス配管と間にバイパス配管を設け、このバイパス配管中にバイパスされるガス冷媒と室外側熱交換器出口の液冷媒とが熱交換する熱交換器（熱回収熱交換器）を設け、さらにその下流側にキャピラリーチューブを設けている。なお、この熱交換器は、バイパス配管を流通する低圧ガス冷媒により高圧液冷媒を冷却して、液冷媒を過冷却させて熱回収し、冷凍能力を向上するものである。
【０００３】
【発明が解決しようとする課題】
ところが、この従来の空気調和装置では、気液分離器からガス冷媒に混じって液冷媒が流出した場合、その液冷媒は熱交換器で蒸発してガス冷媒となり、キャピラリーチュ−ブにはガス冷媒のみが流通することになる。また、冷媒の単位体積あたりの圧力損失は、図１３に示すように、乾き度が０．０５から０．３の範囲で大きく、乾き度が１．０近くになると小さくなっている。したがって、バイパス配管を流通する冷媒の流通抵抗は、気液分離器からガス冷媒のみが流出している場合と気液分離器から液冷媒が混入して流出する場合とでは、あまり変わらないといえる。このため、従来のものでは、気液分離器からバイパス配管に液冷媒が流出し始めた場合、この液冷媒は熱回収熱交換器で気化されてガス冷媒となってキャピラリーチューブに流通し、バイパス配管の冷媒流通抵抗がそれほど増加せず、バイパス配管への液冷媒の流出を止めることができない。したがって、この液冷媒の流出分、冷凍能力の向上を図ることができないという問題のあることが分かった。
【０００４】
この発明は、このような従来技術に存在する問題点に着目してなされたものである。その目的とするところは、液冷媒が気液分離器から圧縮機の低圧側にバイパスすることを防止して、冷凍能力のより一層の向上を図った空気調和装置を提供することにある。
【０００５】
【課題を解決するための手段】
上記目的を達成するために、本発明は、圧縮機、凝縮器、第１冷媒流量制御装置、蒸発器を主な構成部品として備え、これら構成部品を順次主配管で接続した空気調和装置であって、第１冷媒流量制御装置と蒸発器との間に接続した気液分離器と、第２冷媒流量制御装置を備え、かつ、この第２冷媒流量制御装置の一端を気液分離器に接続し、その他端を蒸発器から圧縮機に至る主配管に接続した第１バイパス配管とを備え、第１バイパス配管における第２冷媒流量制御装置の下流側に、凝縮器を流出した後の冷媒とこの第１バイパス配管を流通する冷媒とを熱交換する熱回収熱交換器を設け、この熱回収熱交換器から第１冷媒流量制御装置に至る主配管と、第２冷媒流量制御装置から熱回収熱交換器に至る第１バイパス配管との間に第２バイパス配管を設け、この第２バイパス配管中に第３冷媒流量制御装置を設けたものである。
【０００７】
また、前記気液分離器は、本体容器を有し、前記第１冷媒流量制御装置からこの気液分離器に至る配管の接続部が前記本体容器に対し水平または上向きとなるように形成してもよい。
【０００８】
また、前記気液分離器は、本体容器を有し、この気液分離器から前記蒸発器に至る配管の接続部が前記本体容器の下部に接続されているように形成しても良い。
【０００９】
また、前記気液分離器は、本体容器を有し、この本体容器内における前記第１冷媒流量制御装置からこの気液分離器に至る配管の接続部とこの気液分離器から前記蒸発器に至る配管の接続部との間に、気液分離部材を有するように構成したものでも良い。
【００１０】
また、前記気液分離器は、前記第１バイパス配管の接続部と前記気液分離器から前記蒸発器に至る配管の接続部とを上下に連結し、この連結部に対し、第１冷媒流量制御装置からこの気液分離器に至る配管の接続部を水平方向に接続したものとしても良い。
【００１１】
【発明の実施の形態】
実施形態１．
以下、この発明を具体化した実施の形態１について図１および図２に基づいて説明する。なお、図１は実施の形態１に係る空気調和装置の冷媒回路図であり、図２はこの空気調和装置についての動作を説明するための圧力−エンタルピ線図である。
【００１２】
図１に示す空気調和器は、圧縮機２、凝縮器３、第１冷媒流量制御装置（この場合膨張弁）４、複数個の熱交換器からなる蒸発器５を主な構成部品とし、これら構成部品を主配管６で順次接続したものである。
【００１３】
また、この空気調和装置において、１０は第１冷媒流量制御装置４と蒸発器５との間に接続した気液分離器であり、１１は第１バイパス配管である。この第１バイパス配管１１は、第２冷媒流量制御装置（この場合キャピラリーチューブ）１２を有し、この第２冷媒流量制御装置の一方を気液分離器１０に接続し、他方を蒸発器５から圧縮機２に至る主配管６に接続し、気液分離器１０内のガス冷媒を圧縮機２の吸入側にバイパスさせるためのものである。
【００１４】
次に、このように構成された空気調和装置の動作を、図２を参照しながら説明する。
圧縮機２から吐出された高温高圧のガス冷媒（図中ａ）は、凝縮器３で空気などの冷却流体と熱交換して凝縮し、高温高圧の液冷媒（図中ｂ）に変化する。そして、第１冷媒流量制御装置４により低温低圧の湿り蒸気（気液混合の冷媒）に変化（図中ｃ）し、気液分離器１０に流入する。気液分離器１０に流入した湿り蒸気は液冷媒（図中ｄ）とガス冷媒（図中ｅ）に分離され、液冷媒（図中ｄ）は主配管６を通り蒸発器５に供給され、蒸発器５における圧力損失によって圧力が低下しながら空気などの被冷却物と熱交換して蒸発気化し、圧縮機２に戻る（図中ｆ）。一方、第１バイパス配管１１に流入したガス冷媒（図中ｅ）は、第２冷媒流量制御装置１２でわずかに減圧され、蒸発器５出口の低圧ガス冷媒と合流して圧縮機２に戻る（図中ｆ）。
【００１５】
上記のようなサイクルにおいて、気液分離器１０で十分に液冷媒とガス冷媒の分離ができず、ガス冷媒と液冷媒との混合流体が第１バイパス配管１１に流入した場合には、前記図１３で説明したように乾き度０．０５から０．３において冷媒の流通抵抗が大きくなるため、第２冷媒流量制御装置１２における冷媒の圧力損失は、上記混合流体の場合の方がガス冷媒のみの場合よりも大きくなる。したがって第１バイパス配管１１に液冷媒が流出した場合、第２冷媒流量制御装置１２において急激な圧力損失を生じ、第１バイパス配管１１を流れる冷媒流量が急激に低下し、気液分離器１０から第１バイパス配管１１への液冷媒の流出が抑制される。
【００１６】
この実施の形態１では、蒸発器５は被冷却物が空気である場合について説明したが、この被冷却物は空気のみに限定されない。例えば、安価な夜間電力を利用して、水を冷却して氷を生成し、昼間この氷の冷熱を利用して冷房を行う氷蓄熱装置における製氷用熱交換器のように水を被冷却物とするものでも良い。
【００１７】
実施の形態２．
次に、実施の形態２について図３および図４に基づき説明する。なお、図３は実施の形態２に係る空気調和装置の冷媒回路図であり、図４はこの空気調和装置についての動作を説明するための圧力−エンタルピ線図である。
【００１８】
図３において、主配管６の経路は、前記実施の形態１の場合と同一であって、圧縮機２、凝縮器３、第１冷媒流量制御装置（この場合膨張弁）４、蒸発器５を主な構成部品とし順次接続されている。また、実施の形態１の場合と同様に、第１冷媒流量制御装置４と蒸発器５との間に気液分離器１０が設けられ、さらに、気液分離器１０と蒸発器５から圧縮機２に至る主配管６との間に第２冷媒流量制御装置（この場合キャピラリーチューブ）２１を介装した第１バイパス配管２０が設けられている。
【００１９】
ただし、この第１バイパス配管２０における第２冷媒流量制御装置２１の下流側には、実施の形態１の場合と異なり、第１バイパス配管中を流通する低圧低温の冷媒と凝縮器３から流出した高圧高温の液冷媒とが熱交換する熱回収用熱交換器２２が設けられている。なお、この熱回収熱交換器２２は、第１バイパス配管内を流通する低圧低温の冷媒により凝縮器３から流出した高圧高温の液冷媒を過冷却して、バイパスされる低圧冷媒の冷熱を回収し、冷凍能力を向上させるものである。
【００２０】
また、この実施の形態２では、主配管６における熱回収熱交換器２２から第１冷媒流量制御装置４に至る配管と、第１バイパス配管２０における第２冷媒流量制御装置２１から熱回収熱交換器２２に至る配管との間に、第２バイパス配管２３を設け、この第２バイパス配管２３中に第３冷媒流量制御装置（この場合膨張弁）２４を設けている。
【００２１】
次に、このような構成を有する第２実施の形態に係る空気調和装置の動作を図４を参照しながら説明する。
圧縮機２から吐出された高温高圧のガス冷媒（図中ａ）は、凝縮器３で空気などの冷却流体と熱交換して凝縮し、高温高圧の液冷媒（図中ｂ）に変化する。この液冷媒は熱回収熱交換器２２で過冷却された後（図中ｃ）、大半の冷媒は第１冷媒流量制御装置４に流通し、この第１冷媒流量制御装置４により低温低圧の液冷媒とガス冷媒とが混合した湿り蒸気に変化（図中ｄ）し、気液分離器１０に流入する。そして、気液分離器１０に流入した湿り蒸気は、ガス冷媒（図中ｆ）と液冷媒（図中ｅ）に分離され、液冷媒（図中ｅ）は主配管６を通り蒸発器５に供給され、蒸発器５における圧力損失によって圧力が下がりながら空気などと熱交換して蒸発し、低温低圧のガス冷媒に変化し、圧縮機２ヘ流れる（図中ｉ）。
【００２２】
一方、凝縮器３を流出した液冷媒（図中ｃ）の残部は、第２バイパス配管２３に流入し、第３冷媒流量制御装置２４により低温低圧の湿り蒸気に変化し（図中ｇ）、第１バイパス配管２０を流れるガス冷媒と合流する（図中ｈ）。
また、気液分離器１０で気液分離されたガス冷媒（図中ｆ）は、第１バイパス配管２０に流入し、第２冷媒流量制御装置２１でわずかに減圧され（図中ｊ）、第２バイパス配管２３から流入する湿り蒸気（図中ｇ）と合流する（図中ｈ）。そして、熱回収熱交換器２２で主配管６を流れる液冷媒と熱交換しながら蒸発し（図中ｉ）、主配管６を流通する冷媒と合流して（図中ｉ）、圧縮機２に戻る（図中ｉ）。
【００２３】
実施の形態２では以上のように構成されているため、実施の形態１における場合と同様、気液分離器１０で十分に液冷媒とガス冷媒とに分離できず、ガス冷媒と液冷媒との混合流体が第１バイパス配管２０に流入した場合には、第２冷媒流量制御装置２１で急激な圧力損失を生じ、気液分離器１０から第１バイパス配管２０への液冷媒の流出が防止される。
【００２４】
また、気液分離器１０からのガス冷媒のみを熱回収用熱交換器２２に流通させる場合と比較すると、この実施の形態２のように熱回収熱交換器２２に液冷媒をバイパスさせた場合には、熱回収熱交換器２２内での冷媒の流速が増加し、熱交換性能が向上し、蒸発器５仁尾くる冷媒量を少なくすることによる圧損低減とバイパスによる能力損失分の回収を両立するための熱回収熱交換器２２の小型化が図れる。
【００２５】
この実施の形態２では、蒸発器５は被冷却物が空気である場合について説明したが、この被冷却物は空気のみに限定されない。例えば、安価な夜間電力を利用して、水を冷却して氷を生成し、昼間この氷の冷熱を利用して冷房を行う氷蓄熱装置における製氷用熱交換器のように水を被冷却物とするものでも良い。
【００２６】
【実施例】
次に、上記実施の形態１および実施の形態２に適用される気液分離器の具体的な構造について説明する。
【００２７】
実施例１．
実施例１に係る気液分離器を図５に示す。図５において、１０ａは第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部、１０ｂは気液分離器１０から蒸発器５に至る配管の接続部、１０ｃは第１バイパス配管１１、２０の接続部であり、１０ｄは円筒状の本体容器である。また、これら接続部１０ａ、１０ｂ、１０ｃに付した矢印はそれぞれにおける冷媒の流通方向を示す。この構造の気液分離器１０では、蒸発器５への冷媒が気液分離器１０の下部（すなわち、本体容器１０ｄの下部）から下向きに流出するように導出されているので、蒸発器５に流通する冷媒中にガス冷媒が混ざりにくいという効果がある。
【００２８】
実施例２．
実施例２に係る気液分離器を図６に示す。図中に付された符号および矢印は実施例１と同様である。この場合は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａを下方から導入するとともに、気液分離器１０から蒸発器５に至る配管の接続部１０ｂを本体容器１０ｄの下部から下向きに導出しているので、実施例１と同様の効果があるとともに、気液分離器１０における気液分離効果が向上する。
【００２９】
実施例３．
実施例３に係る気液分離器を図７に示す。図中に付された符号および矢印は実施例１と同様である。この場合は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａを横方向から本体容器１０ｄに導入するとともに、気液分離器１０から蒸発器５に至る配管の接続部１０ｂを本体容器１０ｄの下部から下向きに導出し、第１バイパス配管１１、２０の接続部１０ｃを気液分離器１０の上部（すなわち、本体容器１０ｄの上部）から上方に向けて導出しているので、実施例１と同様の効果があるとともに、気液分離器１０における気液分離効果がより向上する。
【００３０】
実施例４．
実施例４に係る気液分離器を図８に示す。図中に付された符号および矢印は実施例１と同様である。この実施例４は、側断面図は実施例３と同様である。すなわち、気液分離器１０から蒸発器５に至る配管の接続部１０ｂを本体容器１０ｄの下部から下向きに導出し、第１バイパス配管１１、２０の接続部１０ｃを本体容器１０ｄの上部から上方に向けて導出し、さらに、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａを本体容器１０ｄに対し横方向から導入する点では実施例３と同様であるが、この接続部１０ａを気液分離器１０の円筒状本体１０ｄの内壁の接線方向とすることにより、第１冷媒流量制御装置４から気液分離器１０に導入される気液混合の湿り蒸気を本体容器１０ｄ内で旋回させることにより、気液分離効果をより一層向上させたものである。
【００３１】
実施例５．
実施例５に係る気液分離器を図９に示す。図中に付された符号および矢印は実施例１と同様である。この実施例５は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａ、気液分離器１０から蒸発器５に至る配管の接続部１０ｂ、および第１バイパス配管１１、２０の接続部１０ｃの構成は実施例１と同様であるが、気液分離器１０内（すなわち、本体容器１０ｄ内）の中間より下方の高さ部に水平断面全体にわたる多孔板、邪魔板、多孔質材料などからなり、衝突効果により湿り冷媒中の液滴を分離する気液分離部材２５を設けたものである。したがって、この実施例５の場合には、先の実施例１に比しより一層気液分離効果を向上させることができる。
【００３２】
実施例６．
実施例６に係る気液分離器を図１０に示す。図中に付された符号および矢印は実施例１と同様である。この実施例６は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａ、気液分離器１０から蒸発器５に至る配管の接続部１０ｂ、および第１バイパス配管１１、２０の接続部１０ｃの構成は実施例２と同様であるが、気液分離器１０内の下部において、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａと気液分離器１０から蒸発器５に至る配管の接続部１０ｂとの間に、多孔板、邪魔板、多孔質材料などからなる衝突効果により気液分離作用をなす気液分離部材２６を立設したものである。したがって、この実施例６の場合には、先の実施例２に比しより一層気液分離効果を向上させることができる。
【００３３】
実施例７．
実施例７に係る気液分離器を図１１に示す。図中に付された符号および矢印は実施例１と同様である。この実施例７は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａ、気液分離器１０から蒸発器５に至る配管の接続部１０ｂ、および第１バイパス配管１１、２０の接続部１０ｃを図示のごとくＴ字型に組み合わせることにより気液分離器１０を構成したものものである。すなわち、この実施例７の気液分離器１０は、第１バイパス配管１１、２０の接続部１０ｃと気液分離器１０から蒸発器５に至る配管の接続部１０ｂとを直立状の配管に構成し、その分岐点に水平方向から第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａを接続したものである。
【００３４】
このように構成することにより、第１冷媒流量制御装置４から流れてきた気液混合冷媒（湿り冷媒）が接続部１０ｂおよび１０ｃを構成する管壁に衝突して気液分離され、液冷媒がこの接続部１０ｂ内の管壁に沿って下方に流れて蒸発器５に流出し、また、ガス冷媒が接続部１０ｃ内を上昇して第１バイパス配管１１、２０へ流出する。
したがって、この実施例７の場合には、先の実施例１〜６の容器型気液分離器の場合に比し気液分離効果を低下させることなく、コストを低減することができる。
【００３５】
実施例８．
実施例８に係る気液分離器を図１２に示す。図中に付された符号および矢印は実施例１と同様である。この実施例８は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａ、気液分離器１０から蒸発器５に至る配管の接続部１０ｂ、および第１バイパス配管１１、２０の接続部１０ｃを図示のごとくＴ字型に組み合わせることにより気液分離器１０を構成したものものである。すなわち、この実施例８の気液分離器１０は、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａと第１バイパス配管１１、２０の接続部１０ｃとを直立状の配管に構成し、気液分離器１０から蒸発器５に至る配管の接続部１０ｂをこの直立状の配管部における接続部１０ｂと１０ｃとの接合点から水平に分岐したものである。
【００３６】
このように構成することにより、第１冷媒流量制御装置４から流れてきた気液混合冷媒の流れは、液冷媒が接続部１０ａ内の管壁に沿って流れ、ガス冷媒が接続部１０ａ内の管中央を流れる環状流となり、液冷媒を多く含む冷媒が水平方向に分岐された気液分離器１０から蒸発器５に至る配管の接続部１０ｂ内に流出されていく。
したがって、この実施例８の場合には、先の実施例１〜６の容器型気液分離器の場合に比し、また、先の実施例７の場合に比し、気液分離効果は低下するが、コストを低減できる点は実施例７の場合と同様である。また、他の要素部品の配置等から先の実施例７を採用できない場合に必要となることが想定される。
【００３７】
実施例９．
実施例９に係る気液分離器を図１３に示す。この実施例９は、実施例７における第１バイパス配管１１、２０の接続部１０ｃ内に多孔板、邪魔板、多孔質材料などからなり、衝突効果により湿り冷媒中の液滴を分離する気液分離部材２７を設けたものであって、その他の構成は実施例７と同一であり、実施例７と共通する部分には同一の符号および矢印付している。
したがって、この実施例９によれば、気液分離器１０からバイパスされる冷媒は、気液分離部材２７を通して流出することになるので、実施例７に比し、気液分離器１０における気液分離効果がさらに向上する。
【００３８】
実施例１０．
実施例１０に係る気液分離器を図１４に示す。この実施例１０は、実施例７において、第１冷媒流量制御装置４から気液分離器１０に至る配管の接続部１０ａ、気液分離器１０から蒸発器５に至る配管の接続部１０ｂ、および第１バイパス配管１１、２０の接続部１０ｃをＴ字型に結合する結合部に、多孔板、邪魔板、多孔質材料などからなり、衝突効果により湿り冷媒中の液滴を分離する気液分離部材２８を設けたものであって、その他の構成は実施例７と同一であり、実施例７と共通する部分には同一の符号および矢印付している。
したがって、この実施例１０によれば、前記接続部１０ａから流入する湿り冷媒は、この気液分離部材２７における衝突効果による気液分離作用により気液分離され、この気液分離部材２７を通して分岐されて流出することになるので、実施例７に比し、気液分離器１０における気液分離効果がさらに向上する。
【００３９】
【発明の効果】
この発明は以上のように構成されているため、次のような効果を奏する。
本発明によれば、圧縮機、凝縮器、第１冷媒流量制御装置、蒸発器を主な構成部品として備え、これら構成部品を順次主配管で接続した空気調和装置であって、第１冷媒流量制御装置と蒸発器との間に接続した気液分離器と、第２冷媒流量制御装置を備え、かつ、この第２冷媒流量制御装置の一端を気液分離器に接続し、その他端を蒸発器から圧縮機に至る主配管に接続した第１バイパス配管とを備えたものであるので、ガス冷媒が蒸発器に流出されることを防止するとともに、液冷媒が気液分離器から圧縮機の低圧側にバイパスされることを防止して、高効率で信頼性の高い運転を行うことができる。
また、第１バイパス配管における第２冷媒流量制御装置の下流側に、凝縮器を流出した後の冷媒とこの第１バイパス配管を流通する冷媒とを熱交換する熱回収熱交換器を設け、この熱回収熱交換器から第１冷媒流量制御装置に至る主配管と、第２冷媒流量制御装置から熱回収熱交換器に至る第１バイパス配管との間に第２バイパス配管を設け、この第２バイパス配管中に第３冷媒流量制御装置を設けたものであるので、第１の発明と同様の効果を奏することができながら、凝縮器から流出する液冷媒を効率良く過冷却させて冷凍能力を向上させることができる。
【００４１】
また、前記気液分離器は、本体容器を有し、前記第１冷媒流量制御装置からこの気液分離器に至る配管の接続部が前記本体容器に対し水平または上向きとなるように形成されているので、気液分離器における気液分離効率が向上し、冷凍能力が向上する。
【００４２】
また、前記気液分離器は、本体容器を有し、この気液分離器から前記蒸発器に至る配管の接続部が前記本体容器の下部に接続されているので、気液分離器における分離効率が向上し、気液分離器における気液分離効率が向上し、冷凍能力が向上する。
【００４３】
また、前記気液分離器は、本体容器を有し、この本体容器内における前記第１冷媒流量制御装置からこの気液分離器に至る配管の接続部とこの気液分離器から前記蒸発器に至る配管の接続部との間に、気液分離部材を有するので、気液分離器における分離効率が向上し、冷凍能力が向上する。
【００４４】
また、前記気液分離器は、前記第１バイパス配管の接続部と前記気液分離器から前記蒸発器に至る配管の接続部とを上下に連結し、この連結部に対し、第１冷媒流量制御装置からこの気液分離器に至る配管の接続部を水平方向に接続してなるので、気液分離器における分離効率が向上し、冷凍能力が向上する。また、気液分離器は簡易な構造となるのでコストを低減することができる。
【図面の簡単な説明】
【図１】実施の形態１に係る空気調和装置の冷媒回路図である。
【図２】実施の形態１に係る空気調和装置についての動作を説明するための圧力−エンタルピ線図である。
【図３】実施の形態２に係る空気調和装置の冷媒回路図である。
【図４】実施の形態１に係る空気調和装置についての動作を説明するための圧力−エンタルピ線図である。
【図５】実施例１に係る気液分離器の構造図である。
【図６】実施例２に係る気液分離器の構造図である。
【図７】実施例３に係る気液分離器の構造図である。
【図８】実施例４に係る気液分離器の構造図である。
【図９】実施例５に係る気液分離器の構造図である。
【図１０】実施例６に係る気液分離器の構造図である。
【図１１】実施例７に係る気液分離器の構造図である。
【図１２】実施例８に係る気液分離器の構造図である。
【図１３】実施例９に係る気液分離器の構造図である。
【図１４】実施例１０に係る気液分離器の構造図である。
【図１５】冷媒がＲ２２である場合の単位体積あたりの圧力損失を乾き度との関係で示した図である。
【符号の説明】
２圧縮機、３凝縮器、４第１冷媒流量制御装置、５蒸発器、６主配管、１０気液分離器、１０ａ第１冷媒流量制御装置から気液分離器に至る配管の接続部、１０ｂ気液分離器から蒸発器に至る配管の接続部、１０ｃ第１バイパス配管の接続部、１０ｄ円筒状本体、１１、２０第１バイパス配管、１２、２４第２冷媒流量制御装置、２１第２冷媒流量制御装置、２２熱回収熱交換器、２３第２バイパス配管、２４第３冷媒流量制御装置、２５、２６、２７，２８気液分離部材。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air conditioner.
[0002]
[Prior art]
As a conventional air conditioner, a gas-liquid separator is provided between the pressure reducer and the indoor heat exchanger, and the low-pressure refrigerant decompressed by the pressure reducer is gas-liquid separated (about 20% is gas refrigerant and the remaining about 80% This separated gas refrigerant (this gas refrigerant has no latent heat and therefore does not contribute much to the refrigeration capacity) is directly circulated to the intake side of the compressor, and is supplied to the indoor heat exchanger. Some liquid refrigerants are circulated without circulated, and in this way, pressure loss in low-pressure side pipes such as indoor heat exchangers and connection pipes is reduced to improve the refrigerating capacity. . As such a conventional air conditioner, for example, the one described in JP-A-9-310925 is known.
In this air conditioner, as described in the publication, a bypass pipe is provided between the gas-liquid separator and the low-pressure gas pipe on the compressor suction side, and the gas refrigerant bypassed in the bypass pipe and the outdoor heat A heat exchanger (heat recovery heat exchanger) for exchanging heat with the liquid refrigerant at the exchanger outlet is provided, and a capillary tube is further provided on the downstream side. In this heat exchanger, the high pressure liquid refrigerant is cooled by the low pressure gas refrigerant flowing through the bypass pipe, and the liquid refrigerant is supercooled to recover heat, thereby improving the refrigerating capacity.
[0003]
[Problems to be solved by the invention]
However, in this conventional air conditioner, when the liquid refrigerant flows out of the gas-liquid separator and is mixed with the gas refrigerant, the liquid refrigerant evaporates in the heat exchanger to become a gas refrigerant, and the capillary tube has a gas refrigerant. Only will be distributed. Further, as shown in FIG. 13, the pressure loss per unit volume of the refrigerant is large when the dryness is in the range of 0.05 to 0.3, and is small when the dryness is close to 1.0. Therefore, it can be said that the flow resistance of the refrigerant flowing through the bypass pipe is not much different between the case where only the gas refrigerant is flowing out from the gas-liquid separator and the case where the liquid refrigerant is mixed out from the gas-liquid separator. . For this reason, in the prior art, when the liquid refrigerant starts to flow out from the gas-liquid separator to the bypass pipe, the liquid refrigerant is vaporized by the heat recovery heat exchanger and becomes a gas refrigerant, which is circulated through the capillary tube. The refrigerant flow resistance of the pipe does not increase so much, and the outflow of the liquid refrigerant to the bypass pipe cannot be stopped. Therefore, it has been found that there is a problem that the outflow of the liquid refrigerant and the refrigerating capacity cannot be improved.
[0004]
The present invention has been made paying attention to such problems existing in the prior art. An object of the present invention is to provide an air conditioner that prevents the liquid refrigerant from bypassing from the gas-liquid separator to the low pressure side of the compressor and further improves the refrigeration capacity.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, the present invention is an air conditioner comprising a compressor, a condenser, a first refrigerant flow control device, and an evaporator as main components, and these components are sequentially connected by a main pipe. A gas-liquid separator connected between the first refrigerant flow control device and the evaporator, and a second refrigerant flow control device, and one end of the second refrigerant flow control device is connected to the gas-liquid separator. And a first bypass pipe connected to the main pipe from the evaporator to the compressor at the other end, and the refrigerant after flowing out of the condenser on the downstream side of the second refrigerant flow control device in the first bypass pipe; A heat recovery heat exchanger for exchanging heat with the refrigerant flowing through the first bypass pipe is provided, the main pipe extending from the heat recovery heat exchanger to the first refrigerant flow control device, and the heat recovery from the second refrigerant flow control device. The second bar is connected to the first bypass pipe leading to the heat exchanger. Pass pipe is provided, in the second bypass pipe is provided with a third refrigerant flow rate control device.
[0007]
Further, the gas-liquid separator has a main body container, and a connection portion of a pipe from the first refrigerant flow control device to the gas-liquid separator is formed to be horizontal or upward with respect to the main body container. Also good.
[0008]
Further, the gas-liquid separator may have a main body container, and a connection portion of a pipe from the gas-liquid separator to the evaporator may be connected to a lower portion of the main body container.
[0009]
In addition, the gas-liquid separator has a main body container, and a pipe connection portion from the first refrigerant flow control device to the gas-liquid separator in the main body container and the vapor-liquid separator to the evaporator. It may be configured so as to have a gas-liquid separation member between the connecting portions of the pipes to reach.
[0010]
The gas-liquid separator vertically connects a connection portion of the first bypass pipe and a connection portion of the pipe from the gas-liquid separator to the evaporator, and the first refrigerant flow rate is connected to the connection portion. It is good also as what connected the connection part of the piping from a control apparatus to this gas-liquid separator in the horizontal direction.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
Embodiment 1. FIG.
Embodiment 1 of the present invention will be described below with reference to FIGS. 1 and 2. FIG. 1 is a refrigerant circuit diagram of the air-conditioning apparatus according to Embodiment 1, and FIG. 2 is a pressure-enthalpy diagram for explaining the operation of the air-conditioning apparatus.
[0012]
The air conditioner shown in FIG. 1 includes a compressor 2, a condenser 3, a first refrigerant flow control device (in this case, an expansion valve) 4, and an evaporator 5 including a plurality of heat exchangers as main components. The components are sequentially connected by the main pipe 6.
[0013]
In this air conditioner, 10 is a gas-liquid separator connected between the first refrigerant flow control device 4 and the evaporator 5, and 11 is a first bypass pipe. The first bypass pipe 11 has a second refrigerant flow control device (capillary tube in this case) 12, one of the second refrigerant flow control devices is connected to the gas-liquid separator 10, and the other is connected to the evaporator 5. The gas refrigerant in the gas-liquid separator 10 is connected to the main pipe 6 leading to the compressor 2 and is bypassed to the suction side of the compressor 2.
[0014]
Next, the operation of the air conditioner configured as described above will be described with reference to FIG.
The high-temperature and high-pressure gas refrigerant (a in the figure) discharged from the compressor 2 is condensed by exchanging heat with a cooling fluid such as air in the condenser 3 and changed into a high-temperature and high-pressure liquid refrigerant (b in the figure). Then, the first refrigerant flow control device 4 changes to low-temperature and low-pressure wet steam (gas-liquid mixed refrigerant) (c in the figure) and flows into the gas-liquid separator 10. The wet steam flowing into the gas-liquid separator 10 is separated into a liquid refrigerant (d in the figure) and a gas refrigerant (e in the figure), and the liquid refrigerant (d in the figure) is supplied to the evaporator 5 through the main pipe 6. While the pressure is reduced due to the pressure loss in the evaporator 5, it exchanges heat with an object to be cooled such as air to evaporate and returns to the compressor 2 (f in the figure). On the other hand, the gas refrigerant (e in the figure) flowing into the first bypass pipe 11 is slightly depressurized by the second refrigerant flow control device 12, merges with the low-pressure gas refrigerant at the outlet of the evaporator 5, and returns to the compressor 2 ( F) in the figure.
[0015]
In the above-described cycle, when the gas-liquid separator 10 cannot sufficiently separate the liquid refrigerant and the gas refrigerant and the mixed fluid of the gas refrigerant and the liquid refrigerant flows into the first bypass pipe 11, As described in FIG. 13, since the flow resistance of the refrigerant increases at a dryness of 0.05 to 0.3, the pressure loss of the refrigerant in the second refrigerant flow control device 12 is only the gas refrigerant in the case of the above mixed fluid. It becomes bigger than the case. Therefore, when the liquid refrigerant flows into the first bypass pipe 11, an abrupt pressure loss occurs in the second refrigerant flow control device 12, and the refrigerant flow rate flowing through the first bypass pipe 11 rapidly decreases, and the gas-liquid separator 10 The outflow of the liquid refrigerant to the first bypass pipe 11 is suppressed.
[0016]
In this Embodiment 1, although the evaporator 5 demonstrated the case where the to-be-cooled object was air, this to-be-cooled object is not limited only to air. For example, using cold night electricity, water is cooled to produce ice, and water is cooled like an ice storage heat exchanger in an ice storage device that cools the ice using the cold heat of the daytime. It may be.
[0017]
Embodiment 2. FIG.
Next, the second embodiment will be described with reference to FIGS. 3 is a refrigerant circuit diagram of the air-conditioning apparatus according to Embodiment 2, and FIG. 4 is a pressure-enthalpy diagram for explaining the operation of the air-conditioning apparatus.
[0018]
In FIG. 3, the route of the main pipe 6 is the same as that of the first embodiment, and the compressor 2, the condenser 3, the first refrigerant flow control device (in this case, the expansion valve) 4, and the evaporator 5 are connected. It is sequentially connected as main components. Further, as in the case of the first embodiment, a gas-liquid separator 10 is provided between the first refrigerant flow control device 4 and the evaporator 5, and the compressor is further connected from the gas-liquid separator 10 and the evaporator 5 to the compressor. A first bypass pipe 20 having a second refrigerant flow control device (capillary tube in this case) 21 is provided between the main pipe 6 and the main pipe 6.
[0019]
However, unlike the case of the first embodiment, the first bypass pipe 20 flows out of the low-pressure and low-temperature refrigerant flowing through the first bypass pipe and the condenser 3 on the downstream side of the second refrigerant flow rate control device 21. A heat recovery heat exchanger 22 for exchanging heat with the high-pressure and high-temperature liquid refrigerant is provided. The heat recovery heat exchanger 22 supercools the high-pressure and high-temperature liquid refrigerant flowing out of the condenser 3 with the low-pressure and low-temperature refrigerant flowing in the first bypass pipe, and recovers the cold heat of the bypassed low-pressure refrigerant. Thus, the refrigeration capacity is improved.
[0020]
Further, in the second embodiment, heat recovery heat exchange from the heat recovery heat exchanger 22 in the main pipe 6 to the first refrigerant flow control device 4 and from the second refrigerant flow control device 21 in the first bypass pipe 20 is performed. A second bypass pipe 23 is provided between the pipe and the pipe 22, and a third refrigerant flow control device (in this case, an expansion valve) 24 is provided in the second bypass pipe 23.
[0021]
Next, the operation of the air conditioner according to the second embodiment having such a configuration will be described with reference to FIG.
The high-temperature and high-pressure gas refrigerant (a in the figure) discharged from the compressor 2 is condensed by exchanging heat with a cooling fluid such as air in the condenser 3 and changed into a high-temperature and high-pressure liquid refrigerant (b in the figure). After the liquid refrigerant is supercooled by the heat recovery heat exchanger 22 (c in the figure), most of the refrigerant flows to the first refrigerant flow control device 4, and the first refrigerant flow control device 4 cools the liquid at low temperature and low pressure. It changes into wet steam in which the refrigerant and the gas refrigerant are mixed (d in the figure) and flows into the gas-liquid separator 10. The wet steam flowing into the gas-liquid separator 10 is separated into a gas refrigerant (f in the figure) and a liquid refrigerant (e in the figure), and the liquid refrigerant (e in the figure) passes through the main pipe 6 to the evaporator 5. It is supplied, evaporates by exchanging heat with air or the like while the pressure decreases due to pressure loss in the evaporator 5, changes to a low-temperature and low-pressure gas refrigerant, and flows to the compressor 2 (i in the figure).
[0022]
On the other hand, the remaining part of the liquid refrigerant (c in the figure) that has flowed out of the condenser 3 flows into the second bypass pipe 23 and is changed to low-temperature and low-pressure wet steam by the third refrigerant flow control device 24 (g in the figure). The gas refrigerant flows through the first bypass pipe 20 (h in the figure).
Further, the gas refrigerant (f in the figure) separated by the gas-liquid separator 10 flows into the first bypass pipe 20, and is slightly decompressed by the second refrigerant flow control device 21 (j in the figure). 2 Merges with wet steam (g in the figure) flowing in from the bypass pipe 23 (h in the figure). The heat recovery heat exchanger 22 evaporates while exchanging heat with the liquid refrigerant flowing through the main pipe 6 (i in the figure), merges with the refrigerant flowing through the main pipe 6 (i in the figure), and enters the compressor 2. Return (i in the figure).
[0023]
Since the second embodiment is configured as described above, similarly to the first embodiment, the gas-liquid separator 10 cannot sufficiently separate the liquid refrigerant and the gas refrigerant. When the mixed fluid flows into the first bypass pipe 20, a sudden pressure loss occurs in the second refrigerant flow control device 21, and the liquid refrigerant is prevented from flowing out from the gas-liquid separator 10 to the first bypass pipe 20. The
[0024]
Further, when only the gas refrigerant from the gas-liquid separator 10 is circulated to the heat recovery heat exchanger 22, the liquid refrigerant is bypassed to the heat recovery heat exchanger 22 as in the second embodiment. The flow rate of the refrigerant in the heat recovery heat exchanger 22 is increased, the heat exchange performance is improved, and both the pressure loss reduction by reducing the amount of refrigerant in the evaporator 5 and the recovery of the capacity loss by bypass are compatible. Therefore, the heat recovery heat exchanger 22 can be downsized.
[0025]
In this Embodiment 2, although the evaporator 5 demonstrated the case where the to-be-cooled object was air, this to-be-cooled object is not limited only to air. For example, using cold night electricity, water is cooled to produce ice, and water is cooled like an ice storage heat exchanger in an ice storage device that cools the ice using the cold heat of the daytime. It may be.
[0026]
【Example】
Next, a specific structure of the gas-liquid separator applied to the first embodiment and the second embodiment will be described.
[0027]
Example 1.
A gas-liquid separator according to Example 1 is shown in FIG. In FIG. 5, 10a is a connecting portion of a pipe from the first refrigerant flow control device 4 to the gas-liquid separator 10, 10b is a connecting portion of a pipe from the gas-liquid separator 10 to the evaporator 5, and 10c is a first bypass pipe. 11 and 20, and 10 d is a cylindrical main body container. Moreover, the arrow attached | subjected to these connection part 10a, 10b, 10c shows the distribution direction of the refrigerant | coolant in each. In the gas-liquid separator 10 having this structure, the refrigerant to the evaporator 5 is led out downward from the lower part of the gas-liquid separator 10 (that is, the lower part of the main body container 10d). There is an effect that the gas refrigerant is not easily mixed in the circulating refrigerant.
[0028]
Example 2
A gas-liquid separator according to Example 2 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. In this case, the pipe connection 10a from the first refrigerant flow control device 4 to the gas-liquid separator 10 is introduced from below, and the pipe connection 10b from the gas-liquid separator 10 to the evaporator 5 is connected to the main body container. Since it is derived downward from the lower part of 10d, it has the same effect as in the first embodiment, and the gas-liquid separation effect in the gas-liquid separator 10 is improved.
[0029]
Example 3 FIG.
A gas-liquid separator according to Example 3 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. In this case, the pipe connecting portion 10a leading from the first refrigerant flow control device 4 to the gas-liquid separator 10 is introduced into the main body container 10d from the lateral direction, and the pipe connecting from the gas-liquid separator 10 to the evaporator 5 is connected. The part 10b is led out downward from the lower part of the main body container 10d, and the connection part 10c of the first bypass pipes 11 and 20 is led out upward from the upper part of the gas-liquid separator 10 (that is, the upper part of the main body container 10d). Therefore, the effects similar to those of the first embodiment are obtained, and the gas-liquid separation effect in the gas-liquid separator 10 is further improved.
[0030]
Example 4
A gas-liquid separator according to Example 4 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. The fourth embodiment is the same as the third embodiment in a side sectional view. That is, the connecting portion 10b of the pipe extending from the gas-liquid separator 10 to the evaporator 5 is led downward from the lower portion of the main body container 10d, and the connecting portion 10c of the first bypass pipes 11 and 20 is extended upward from the upper portion of the main body container 10d. This is the same as in the third embodiment in that the connecting portion 10a of the pipe leading from the first refrigerant flow control device 4 to the gas-liquid separator 10 is introduced from the lateral direction into the main body container 10d. By connecting the connecting portion 10a to the tangential direction of the inner wall of the cylindrical main body 10d of the gas-liquid separator 10, the wet vapor of the gas-liquid mixture introduced from the first refrigerant flow control device 4 to the gas-liquid separator 10 is supplied to the main body container. The gas-liquid separation effect is further improved by swirling within 10d.
[0031]
Embodiment 5 FIG.
A gas-liquid separator according to Example 5 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. In the fifth embodiment, a pipe connection portion 10a extending from the first refrigerant flow control device 4 to the gas-liquid separator 10, a pipe connection portion 10b extending from the gas-liquid separator 10 to the evaporator 5, and a first bypass pipe 11 are used. , 20 is the same as that of the first embodiment, but the perforated plate and the baffle plate over the entire horizontal section at the height below the middle in the gas-liquid separator 10 (that is, in the main body container 10d). The gas-liquid separation member 25 is made of a porous material and the like and separates droplets in the wet refrigerant by a collision effect. Therefore, in the case of the fifth embodiment, the gas-liquid separation effect can be further improved as compared with the first embodiment.
[0032]
Example 6
A gas-liquid separator according to Example 6 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. In the sixth embodiment, a connecting portion 10a of a pipe extending from the first refrigerant flow control device 4 to the gas-liquid separator 10, a connecting portion 10b of a pipe extending from the gas-liquid separator 10 to the evaporator 5, and a first bypass pipe 11 are used. , 20 is the same as the configuration of the second embodiment, but in the lower part of the gas-liquid separator 10, the connection portion 10a of the pipe from the first refrigerant flow control device 4 to the gas-liquid separator 10 and the gas are separated. A gas-liquid separation member 26 that performs a gas-liquid separation action by a collision effect made of a perforated plate, a baffle plate, a porous material or the like is erected between the connecting portion 10 b of the pipe from the liquid separator 10 to the evaporator 5. Is. Therefore, in the case of the sixth embodiment, the gas-liquid separation effect can be further improved as compared with the second embodiment.
[0033]
Example 7
A gas-liquid separator according to Example 7 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. In the seventh embodiment, a connecting portion 10a of a pipe extending from the first refrigerant flow control device 4 to the gas-liquid separator 10, a connecting portion 10b of a pipe extending from the gas-liquid separator 10 to the evaporator 5, and a first bypass pipe 11 are used. The gas-liquid separator 10 is configured by combining 20 connecting portions 10c in a T shape as shown in the figure. That is, in the gas-liquid separator 10 of the seventh embodiment, the connection portion 10c of the first bypass pipes 11 and 20 and the connection portion 10b of the pipe extending from the gas-liquid separator 10 to the evaporator 5 are configured as upright pipes. Then, a connecting portion 10a of a pipe from the first refrigerant flow control device 4 to the gas-liquid separator 10 is connected to the branch point from the horizontal direction.
[0034]
With this configuration, the gas-liquid mixed refrigerant (wet refrigerant) flowing from the first refrigerant flow control device 4 collides with the tube walls constituting the connecting portions 10b and 10c to be separated into gas and liquid, and the liquid refrigerant is It flows downward along the tube wall in the connecting portion 10b and flows out to the evaporator 5, and the gas refrigerant rises in the connecting portion 10c and flows out to the first bypass pipes 11 and 20.
Therefore, in the case of this Example 7, cost can be reduced, without reducing the gas-liquid separation effect compared with the case of the container-type gas-liquid separator of previous Examples 1-6.
[0035]
Example 8 FIG.
A gas-liquid separator according to Example 8 is shown in FIG. Reference numerals and arrows given in the drawing are the same as those in the first embodiment. In the eighth embodiment, a connecting portion 10a of a pipe extending from the first refrigerant flow control device 4 to the gas-liquid separator 10, a connecting portion 10b of a pipe extending from the gas-liquid separator 10 to the evaporator 5, and a first bypass pipe 11 are used. The gas-liquid separator 10 is configured by combining 20 connecting portions 10c in a T shape as shown in the figure. That is, in the gas-liquid separator 10 of the eighth embodiment, the connecting portion 10a of the pipe from the first refrigerant flow control device 4 to the gas-liquid separator 10 and the connecting portion 10c of the first bypass pipes 11 and 20 are upright. The connecting portion 10b of the piping from the gas-liquid separator 10 to the evaporator 5 is horizontally branched from the junction of the connecting portions 10b and 10c in this upright piping portion.
[0036]
By configuring in this way, the flow of the gas-liquid mixed refrigerant flowing from the first refrigerant flow control device 4 is such that the liquid refrigerant flows along the tube wall in the connecting portion 10a and the gas refrigerant in the connecting portion 10a. An annular flow flows through the center of the pipe, and a refrigerant containing a large amount of liquid refrigerant flows out into the connecting portion 10b of the pipe from the gas-liquid separator 10 branched in the horizontal direction to the evaporator 5.
Therefore, in the case of this Example 8, compared with the case of the container-type gas-liquid separator of previous Examples 1-6, compared with the case of previous Example 7, the gas-liquid separation effect is reduced. However, the point that the cost can be reduced is the same as in the case of the seventh embodiment. Further, it is assumed that it is necessary when the previous embodiment 7 cannot be adopted due to the arrangement of other element parts.
[0037]
Example 9
A gas-liquid separator according to Example 9 is shown in FIG. In the ninth embodiment, the connection portion 10c of the first bypass pipes 11 and 20 in the seventh embodiment is made of a porous plate, a baffle plate, a porous material, etc., and the gas-liquid that separates droplets in the wet refrigerant by the collision effect. The separation member 27 is provided, and the other configuration is the same as that of the seventh embodiment, and portions common to the seventh embodiment are denoted by the same reference numerals and arrows.
Therefore, according to the ninth embodiment, since the refrigerant bypassed from the gas-liquid separator 10 flows out through the gas-liquid separation member 27, the gas-liquid separator in the gas-liquid separator 10 is compared with the seventh embodiment. The separation effect is further improved.
[0038]
Example 10
FIG. 14 shows a gas-liquid separator according to Example 10. The tenth embodiment is the same as the seventh embodiment in which a pipe connection 10a from the first refrigerant flow control device 4 to the gas-liquid separator 10, a pipe connection 10b from the gas-liquid separator 10 to the evaporator 5, and A gas-liquid separation that consists of a perforated plate, baffle plate, porous material, etc., in the connecting portion 10c connecting the connecting portions 10c of the first bypass pipes 11, 20 in a T-shape, and that separates droplets in the wet refrigerant by a collision effect. The member 28 is provided, and the other configuration is the same as that of the seventh embodiment, and parts common to the seventh embodiment are denoted by the same reference numerals and arrows.
Therefore, according to the tenth embodiment, the wet refrigerant flowing from the connecting portion 10 a is separated into gas and liquid by the gas-liquid separation action due to the collision effect in the gas-liquid separation member 27 and branched through the gas-liquid separation member 27. Therefore, the gas-liquid separation effect in the gas-liquid separator 10 is further improved as compared with the seventh embodiment.
[0039]
【The invention's effect】
Since this invention is comprised as mentioned above, there exist the following effects.
According to the onset bright, compressor, condenser, first refrigerant flow rate control device, an evaporator as main components, an air conditioner which connects these components sequentially in the main pipe, the first refrigerant A gas-liquid separator connected between the flow control device and the evaporator; a second refrigerant flow control device; and one end of the second refrigerant flow control device connected to the gas-liquid separator, and the other end Since the first bypass pipe connected to the main pipe from the evaporator to the compressor is provided, the gas refrigerant is prevented from flowing out to the evaporator and the liquid refrigerant is discharged from the gas-liquid separator to the compressor. Therefore, it is possible to perform a highly efficient and reliable operation.
Further, a heat recovery heat exchanger for exchanging heat between the refrigerant after flowing out the condenser and the refrigerant flowing through the first bypass pipe is provided on the downstream side of the second refrigerant flow control device in the first bypass pipe. A second bypass pipe is provided between the main pipe from the heat recovery heat exchanger to the first refrigerant flow controller and the first bypass pipe from the second refrigerant flow controller to the heat recovery heat exchanger. Since the third refrigerant flow rate control device is provided in the bypass pipe, the refrigeration capacity can be improved by efficiently subcooling the liquid refrigerant flowing out of the condenser while achieving the same effect as the first invention. Can be improved.
[0041]
The front-handed liquid separator includes a main container, the connecting portion of the pipe leading to the gas-liquid separator from the first refrigerant flow rate control device is formed so as to be horizontal or upward relative to the main container Therefore, the gas-liquid separation efficiency in the gas-liquid separator is improved, and the refrigerating capacity is improved.
[0042]
The front-handed liquid separator includes a main container, the connecting portion of the pipe extending to the evaporator from the gas-liquid separator is connected to the lower portion of the main body container, separated in the gas-liquid separator Efficiency improves, the gas-liquid separation efficiency in a gas-liquid separator improves, and a refrigerating capacity improves.
[0043]
The front-handed liquid separator includes a main container, a connecting portion of the pipe extending from the first refrigerant flow rate control device in the body vessel to the gas-liquid separator wherein the evaporator from the gas-liquid separator Since the gas-liquid separation member is provided between the connecting portion of the pipes leading to, the separation efficiency in the gas-liquid separator is improved, and the refrigerating capacity is improved.
[0044]
Further, the prior Kiki liquid separator, connects the connection portion of the pipe extending to the evaporator from the gas-liquid separator and the connecting portion of the first bypass pipe vertically, with respect to the connecting portion, the first refrigerant Since the connecting portion of the pipe from the flow rate control device to the gas-liquid separator is connected in the horizontal direction, the separation efficiency in the gas-liquid separator is improved and the refrigerating capacity is improved. Further, since the gas-liquid separator has a simple structure, the cost can be reduced.
[Brief description of the drawings]
1 is a refrigerant circuit diagram of an air-conditioning apparatus according to Embodiment 1. FIG.
2 is a pressure-enthalpy diagram for explaining the operation of the air-conditioning apparatus according to Embodiment 1. FIG.
FIG. 3 is a refrigerant circuit diagram of the air-conditioning apparatus according to Embodiment 2.
FIG. 4 is a pressure-enthalpy diagram for explaining the operation of the air-conditioning apparatus according to Embodiment 1.
5 is a structural diagram of a gas-liquid separator according to Embodiment 1. FIG.
6 is a structural diagram of a gas-liquid separator according to Embodiment 2. FIG.
FIG. 7 is a structural diagram of a gas-liquid separator according to a third embodiment.
FIG. 8 is a structural diagram of a gas-liquid separator according to a fourth embodiment.
FIG. 9 is a structural diagram of a gas-liquid separator according to a fifth embodiment.
FIG. 10 is a structural diagram of a gas-liquid separator according to a sixth embodiment.
FIG. 11 is a structural diagram of a gas-liquid separator according to a seventh embodiment.
FIG. 12 is a structural diagram of a gas-liquid separator according to an eighth embodiment.
13 is a structural diagram of a gas-liquid separator according to Embodiment 9. FIG.
14 is a structural diagram of a gas-liquid separator according to Embodiment 10. FIG.
FIG. 15 is a diagram showing the pressure loss per unit volume when the refrigerant is R22 in relation to the dryness.
[Explanation of symbols]
2 Compressor, 3 Condenser, 4 First refrigerant flow control device, 5 Evaporator, 6 Main piping, 10 Gas-liquid separator, 10a Pipe connection from the first refrigerant flow control device to the gas-liquid separator, 10b Pipe connection part from gas-liquid separator to evaporator, 10c Connection part of first bypass pipe, 10d Cylindrical body, 11, 20 First bypass pipe, 12, 24 Second refrigerant flow control device, 21 Second refrigerant Flow control device, 22 Heat recovery heat exchanger, 23 Second bypass pipe, 24 Third refrigerant flow control device, 25, 26, 27, 28 Gas-liquid separation member.

Claims

An air conditioner comprising a compressor, a condenser, a first refrigerant flow control device, and an evaporator as main components, and sequentially connecting these components through a main pipe,
A gas-liquid separator connected between the first refrigerant flow control device and the evaporator;
A first refrigerant flow control device is provided, and one end of the second refrigerant flow control device is connected to the gas-liquid separator, and the other end is connected to the main pipe from the evaporator to the compressor. With bypass piping ,
On the downstream side of the second refrigerant flow control device in the first bypass pipe, a heat recovery heat exchanger for exchanging heat between the refrigerant after flowing out the condenser and the refrigerant flowing through the first bypass pipe is provided,
A second bypass pipe between the main pipe from the heat recovery heat exchanger to the first refrigerant flow control device and the first bypass pipe from the second refrigerant flow control device to the heat recovery heat exchanger. And an air conditioner characterized in that a third refrigerant flow rate control device is provided in the second bypass pipe .

The gas-liquid separator has a main body container, and a connection portion of a pipe from the first refrigerant flow control device to the gas-liquid separator is formed to be horizontal or upward with respect to the main body container. The air conditioning apparatus according to claim 1 .

The gas-liquid separator includes a main body container, according to claim 1, the connecting portion of the pipe extending to the evaporator from the gas-liquid separator is characterized in that it is connected to the lower portion of the main container Air conditioner.

The gas-liquid separator has a main body container, and a connecting portion of a pipe from the first refrigerant flow control device to the gas-liquid separator in the main body container and a pipe from the gas-liquid separator to the evaporator The air-conditioning apparatus according to claim 1, further comprising a gas-liquid separation member between the first and second connecting portions.

The gas-liquid separator vertically connects a connecting portion of the first bypass pipe and a connecting portion of a pipe extending from the gas-liquid separator to the evaporator, and the first refrigerant flow control device is connected to the connecting portion. The air conditioner according to claim 1, wherein a connecting portion of a pipe extending from the gas to the gas-liquid separator is connected in a horizontal direction.